Outboard hydrostatic bearing assembly for can bodymaker

ABSTRACT

A hydrostatic/hydrodynamic fluid bearing assembly for a can bodymaker is provided. The hydrostatic/hydrodynamic fluid bearing assembly is separate from the ram body. The outboard guide bearing assembly includes a carriage assembly and a number of elongated journals. The carriage assembly includes a ram coupling, a crank coupling, and body defining a number of journal passages. The ram body is coupled to a ram coupling. The crank coupling is structured to be coupled to a crank arm. Each journal extends through a carriage assembly body journal passage. In this configuration, the ram body may form a can body in a traditional manner, but fluid bearing assembly fluid is not applied to the ram body. Instead, the fluid bearing assembly fluid is applied to the journals.

CROSS REFERENCE TO RELATED APPLICATION

This application is a continuation patent application of U.S. patentapplication Ser. No. 14/993,159, filed Jan. 12, 2016, which applicationis a continuation-in-part application of U.S. patent application Ser.No. 14/470,987, filed Aug. 28, 2014, entitled OUTBOARD HYDROSTATICBEARING ASSEMBLY FOR CAN BODYMAKER, which application claims the benefitof U.S. Patent Application Ser. No. 61/870,831, filed Aug. 28, 2013,which is incorporated by reference herein.

BACKGROUND OF THE INVENTION Field of the Invention

The disclosed and claimed concept relates to a can bodymaker and, morespecifically, to a can bodymaker wherein the ram assembly includesoutboard bearings and a ram body having a reduced length.

Background Information

Generally, an aluminum can begins as a disk of aluminum, also known as a“blank,” that is punched from a sheet or coil of aluminum. That is, thesheet is fed into a dual action press where a “blank” disc is cut fromthe sheet by an outer slide/ram motion. An inner slide/ram then pushesthe “blank” through a draw process to create a cup. The cup has a bottomand a depending sidewall. The cup is fed into one of several bodymakers,which perform a redraw and ironing operation. More specifically, the cupis disposed in a can forming machine at the mouth of a die pack havingsubstantially circular openings therein. The cup is held in place by aredraw sleeve, which is part of the redraw assembly. The redraw sleeveis a hollow tubular construct that is disposed inside the cup and biasesthe cup against the die pack. More specifically, the first die in thedie pack is the redraw die, which is not a part of the redraw assembly.The cup is biased against the redraw die by the redraw sleeve. Otherdies, the ironing dies, are disposed behind, and axially aligned with,the redraw die. The ironing dies and redraw die are not part of theredraw assembly. An elongated, cylindrical ram assembly 1PA (prior art),shown in FIGS. 1 and 1A, includes a carriage 2PA that supports a rambody 3PA with a punch 4PA at the forward, distal end. The ram and punchare aligned with, and structured to travel through, the openings in theredraw die and the ironing dies. At the end of the die pack opposite theram is a domer. The domer is a die structured to form a concave dome inthe bottom of the cup/can.

Thus, in operation, a cup is disposed at one end of the die pack. Thecup, typically, has a greater diameter than a finished can as well as agreater wall thickness. The redraw sleeve is disposed inside of the cupand biases the cup bottom against the redraw die. The opening in theredraw die has a diameter that is smaller than the cup. The elongatedram body, and more specifically the punch, passes through the hollowredraw sleeve and contacts the bottom of the cup. As the ram bodycontinues to move forward, the cup is moved through the redraw die. Asthe opening in the redraw die is smaller than the original diameter ofthe cup, the cup is deformed and becomes elongated with a smallerdiameter. The wall thickness of the cup typically remains the same asthe cup passes through the redraw die. As the ram continues to moveforward, the elongated cup passes through a number of ironing dies. Theironing dies each thin the wall thickness of the cup causing the cup toelongate. The final forming of the can body occurs when the bottom ofthe elongated cup engages the domer, creating a concave dome in the cupbottom. At this point, and compared to the original shape of the cup,the can body is elongated, has a thinner wall, and a domed bottom.

During this operation, heat is created by friction in both the ramassembly and the die pack. This heat is dissipated by a cooling fluidthat passes through and over the surface of the components. The coolingfluid disposed on the surface of the ram body is substantially collectedby a seal assembly disposed between a hydrostatic/hydrodynamic bearingassembly and the redraw (or hold down) assembly. The seal assemblyincludes a number of seals that conform to the cross-sectional shape ofthe ram body. As the ram body passes through the seal assembly, thecooling fluid is collected and recycled.

After the forming operations on the can body are complete, the can bodyis ejected from the ram, and more specifically the punch, for furtherprocessing, such as, but not limited to trimming, washing, printing,flanging, inspecting and placed on pallets, which are shipped to thefiller. At the filler, the cans are taken off of the pallets, filled,ends placed on them and then the filled cans are repackaged in six packsand/or twelve pack cases, etc.

The ram body moves in a cycle many times each minute. To accomplish thismotion, the bodymaker also includes a crank assembly having a crank arm.The crank arm is coupled to the ram assembly and causes the ram assemblyto reciprocate. The ram body is substantially, axially aligned with thehollow redraw sleeve and the die pack. The alignment is importantbecause a mis-alignment causes the ram to wear on the dies andvice-versa. As shown in FIG. 1A, alignment of the ram body is improvedby a hydrostatic/hydrodynamic ram guide assembly 5PA that guides the rambody through the tooling, hereinafter a “ram guide.” There areadditional hydrostatic/hydrodynamic fluid bearing assemblies 6PA on thesides of the ram assembly carriage, but these bearings do not “guide”the ram. These hydrostatic/hydrodynamic fluid bearing assemblies 6PA aredisposed in channels and have ports 7PA, disposed on the top, side, andlower surfaces, that produce a lubricating fluid. Various factors, suchas, but not limited to, the relatively short length of the carriage,wherein the hydrostatic/hydrodynamic fluid bearing assemblies 6 areimmediately adjacent each other, prevent these additionalhydrostatic/hydrodynamic fluid bearing assemblies 6PA from controllingthe orientation and alignment of the ram body. That is, the small amountof “wobble” of the carriage in the channels prevents the carriage andthe hydrostatic/hydrodynamic fluid bearing assemblies 6PA from guidingthe ram body.

Thus, as used herein, a “guide,” when used in reference to a ram bodybearing, means to control the orientation and alignment of the ram body.Thus, a “guide bearing” or “guide bearing assembly,” as used herein, isstructured to, and does, control the orientation and alignment of theram body. A bearing, such as the prior art hydrostatic/hydrodynamicfluid bearing assemblies 6PA on the sides of the ram assembly carriage,that have a minimal influence or are merely capable of affecting theorientation and alignment of the ram body are not “guide” bearingassemblies, as used herein. Stated alternately, and noting that a rambody must be guided, if the ram body has no guide, then the bearingassemblies on the sides of the ram carriage are the “guide bearingassemblies.” If, however, the ram body has a guide, then the bearingassemblies on the sides of the ram carriage are not “guide bearingassemblies.”

The guide bearing assembly is, typically, disposed immediately upstream(closer to the crank arm) of the redraw assembly. The fluid bearingassembly includes a body defining a passage. The ram body extendsthrough the fluid bearing assembly passage. Moreover, the fluid bearingassembly introduces a fluid, such as, but not limited to oil, betweenthe fluid bearing assembly body and the ram body. Controlling the amountand pressure of the fluid allows for precise control over the alignmentof the ram body with the hollow redraw sleeve and the die pack. Thefluid bearing assembly fluid is collected by the seal assembly andrecycled.

The disadvantage to this configuration is that the fluid bearingassembly fluid is not completely removed by the seal assembly. Thus, aportion of the fluid bearing assembly fluid remains on the ram body whenthe cooling fluid is applied. Further, the fluids mix and the collectedcooling fluid becomes contaminated. This also means that the fluidbearing assembly fluid, which may be an expensive oil, is slowly lost.

Another disadvantage is that the ram body must have a sufficient lengthnot only to extend through the die pack, but the seal assembly and fluidbearing assembly; for a can body of a typical 12 fluid ounce can, theram body has a length of between about 50 inches to 52 inches when usinga 24 inch stroke for a can body of a typical 12 fluid ounce can. Ramlengths differ for different stroke lengths to support different sizecan bodies. For example, the following is a table of common ram lengthsand the associated stroke.

Exemplary Ram Length Range A Specific Embodiment Stroke Length 45.0 to46.0 Inches 45.387 Inches  18 Inches 49.0 to 51.813 Inches  50.0 Inches22 Inches 50.0 to 52.0 Inches 51.0 Inches 24 Inches 56.0 to 58.0 Inches57.0 Inches 30 InchesA ram body of any of these lengths is prone to damage from normal wearand tear.

As noted above, the ram body passes through a die pack in a firstdirection when forming a can body, and then travels back through the diepack after the can body is formed. The die pack in the bodymaker hasmultiple, spaced dies, each die having an opening. Each die opening isslightly smaller than the next adjacent upstream die. Because theopenings in the subsequent dies in the die pack have a smaller innerdiameter, i.e., a smaller opening, the aluminum cup is thinned as theram moves the aluminum through the rest of the die pack. The spacebetween the punch and the redraw die is typically a small clearance(0.001-2 inch per side) over metal thickness and is less than 0.004 inchin the last ironing die. Typical aluminum gauge used to create a typical12 fluid ounce can is 0.0108 inch in practice today. This narrowspacing, however, is a disadvantage, especially during the returnstroke.

Ram droop or deflection is inherent to this long slender horizontal ramand punch with stroke lengths varying from 22-30 inches and throughputfrequencies ranging from 210 to 450 strokes/minute (SPM) depending oncan diameter, can height and machine model. In its simplest form, thisram can be visualized as a cantilever beam fixed at one end and free onthe other end. The upper theorized beam type shows the deflection of theram due to the tungsten carbide punch weight and the lower theorizedbeam type shows the deflection of the long steel ram due to its ownweight. The total deflection of the horizontal ram in a known bodymakeris a combination of these two effects. The typical weight of the ram andpunch assembly is approximately 50 lbf total. The maximum deflection (δ)or ram droop is linearly proportional to the weight (point load P ordistributed load ω) of the long slender light weight steel ram(ρ_(steel)=0.284 lb/in³) and heavy tungsten carbide (or WC−ρWC=0.567lb/in³) punch at the end of the ram. However, the maximum deflection orram droop (conceptualized as a cantilever beam) is governed by itslength (l) to the fourth power for the long slender steel ram and to thethird power for the heavy carbide punch at the end of the ram. I is thearea moment of inertia, as is known. Therefore, significant reduction indeflection or ram droop can be realized if the ram could be shortened.The concept to outboard the hydrostatic/hydrodynamic ram bearings fromthe main ram itself is essential to shortening the length of the rambecause the ram no longer requires additional length to be supported bythe bearing through the can body making process. Rain droop is a problemon the return stroke where a can is not being formed. In the returnstroke, the punch and ram have more of a tendency to contact the toolingcausing wear and damage. A significant contributor to this is contactbetween the punch and the ironing dies (primarily third iron or endiron) on the return stroke of the machine.

Further, as noted above, a ram body passes through ahydrostatic/hydrodynamic fluid bearing assembly. Thehydrostatic/hydrodynamic fluid bearing assembly is fixed to a bulkheadin the can bodymaker housing assembly. This means that the length of thecantilevered portion of the ram body changes during the body makingcycle. That is, when the rain body is in a retracted, first position,the length of the cantilevered portion of the ram body is relativelyshort. Conversely, when the ram body is in an extended, second position,the length of the cantilevered portion of the ram body is relativelylong. The dynamic nature of the length of the cantilevered portion ofthe ram body means that the amount of droop changes dynamically as well.This means that a system to compensate for the ram droop would have tobe a dynamic system as well.

Further, ram droop, as well as any other contact between the ram bodyand the die pack cause the ram body to become misaligned with the diepack. Stated alternately, contact between the ram body and the die packcreates an offsetting force acting in various directions about the ramassembly center of gravity. These offsetting forces create a torqueabout the ram assembly center of gravity resulting in the “wobble”discussed above. This is a disadvantage.

There is, therefore, a need for a ram assembly including a ram body thatis less susceptible to ram droop. There is, more specifically, a needfor a ram body having a reduced length. That is, the length of the rambody is a stated problem.

SUMMARY OF THE INVENTION

These needs, and others, are met by at least one embodiment of thisinvention which provides in one embodiment, a ram assembly with a rambody having a diameter of about 2.0 to 2.5 inches, e.g., for a typical12 fluid oz. can, and a length of between about 30.0 inches and 32.0inches, or about 31.0 inches. In another exemplary embodiment, wherein aram seal assembly is used, the ram body has a length of between about33.0 inches to about 36.0 inches, or about 34.5 inches. In thisembodiment, the ram body has a diameter of about 1.5 to about 3.5inches, or about 2.5 inches, for a typical 12 fluid oz. can.

In another embodiment, a can bodymaker ram assembly includes an outboardguide bearing assembly. The outboard guide bearing assembly is“outboard;” that is, as used herein, spaced, from the ram body. Theoutboard guide bearing assembly includes a carriage assembly and abearing assembly. The bearing assembly, in an exemplary embodiment,includes two bearings disposed on the lateral sides of the carriageassembly. In an exemplary embodiment, the bearing assemblies arehydrostatic/hydrodynamic bearing assemblies. Use of an outboard guidebearing assembly allows for a shorter ram body in that the ram body doesnot need to extend through a bearing assembly as well as the die pack.

In another embodiment, a can bodymaker ram assembly includes anelongated, generally hollow ram body and a tension assembly. The rambody includes a proximal end, a medial portion, and a distal end. Thetension assembly includes an elongated support member. The tensionassembly support member includes a proximal end and a distal end. Thetension assembly support member is substantially disposed within the rambody with the tension assembly support member proximal end coupled tothe ram body proximal end, and the tension assembly support memberdistal end coupled to one of the ram body medial portion or the ram bodydistal end.

In another embodiment, the carriage assembly guide bearing assembliesare structured to orient the ram body with the passage through the diepack. That is, the carriage assembly guide bearing assemblies includefluid producing elements that are sufficiently spaced so as to alter theorientation of a ram body, or a punch, in a manner intended to positionthe longitudinal axis of the ram body to move over a selected path oftravel (which is aligned with the longitudinal axis of the die packpassage), and, the carriage assembly guide bearing assemblies produce asufficient, but reasonable, amount of fluid to establish an aligningfluid bearing stiffness.

BRIEF DESCRIPTION OF THE DRAWINGS

A full understanding of the invention can be gained from the followingdescription of the preferred embodiments when read in conjunction withthe accompanying drawings in which:

FIGS. 1 and 1A are isometric views of a prior art ram assembly.

FIG. 1B is a side view of a prior art ram assembly.

FIGS. 2, 3, and 4 show a side cross-sectional view of a bodymaker withthe ram assembly in a first position, an intermediate position, and asecond position, respectively.

FIGS. 5, 6, and 7 show a top view of a bodymaker with the ram assemblyin a first position, an intermediate position, and a second position,respectively.

FIG. 8 is an isometric view of an outboard guide bearing assembly.

FIG. 9 is an isometric view of an outboard carriage assembly.

FIG. 10 is a cross-sectional view of another embodiment of the ram body.

FIG. 10A is a detail cross-sectional view of the medial portion of theram body.

FIG. 10B is a detail cross-sectional view of the proximal end of the rambody.

FIG. 11 is a first isometric view of another embodiment of an outboardguide bearing assembly.

FIG. 12 is a second isometric view of another embodiment of an outboardguide bearing assembly.

FIG. 13 is a top view of another embodiment of an outboard guide bearingassembly.

FIG. 14 is a cross-sectional view of another embodiment of the ram body.

FIG. 14A is a detail cross-sectional view of another embodiment of themedial and distal portions of the ram body.

FIG. 15 is a top view of another embodiment of an outboard guide bearingassembly.

FIG. 16 is a cross-sectional view of an outboard guide bearing assembly.

FIG. 17 is a table showing a formula for ram deflection.

FIG. 18 is a table showing a formula for cantilever beam load.

FIG. 19 is an isometric view of an alternate embodiment.

FIG. 20 is another isometric view of an alternate embodiment.

FIG. 21 is an isometric exploded view of an alternate embodiment.

FIG. 22A is a top view of a ram assembly indicating the center ofgravity of the ram assembly.

FIG. 22B is a side view of a ram assembly indicating the center ofgravity of the ram assembly.

FIG. 22C is a front view of a ram assembly indicating the center ofgravity of the ram assembly.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Directional phrases used herein, such as, for example, clockwise,counterclockwise, left, right, top, bottom, upwards, downwards andderivatives thereof, relate to the orientation of the elements shown inthe drawings and are not limiting upon the claims unless expresslyrecited therein.

As used herein, the singular form of “a,” “an,” and “the” include pluralreferences unless the context clearly dictates otherwise.

As used herein, the statement that two or more parts or components are“coupled” shall mean that the parts are joined or operate togethereither directly or indirectly, i.e., through one or more intermediateparts or components, so long as a link occurs. As used herein, “directlycoupled” means that two elements are directly in contact with eachother. As used herein, “fixedly coupled” or “fixed” means that twocomponents are coupled so as to move as one while maintaining a constantorientation relative to each other. Accordingly, when two elements arecoupled, all portions of those elements are coupled. A description,however, of a specific portion of a first element being coupled to asecond element, e.g., an axle first end being coupled to a first wheel,means that the specific portion of the first element is disposed closerto the second element than the other portions thereof. Further, anobject resting on another object held in place only by gravity is not“coupled” to the lower object unless the upper object is otherwisemaintained substantially in place. That is, for example, a book on atable is not coupled thereto, but a book glued to a table is coupledthereto.

As used herein, the statement that two or more parts or components“engage” one another shall mean that the elements exert a force or biasagainst one another either directly or through one or more intermediateelements or components.

As used herein, the word “unitary” means a component is created as asingle piece or unit. That is, a component that includes pieces that arecreated separately and then coupled together as a unit is not a“unitary” component or body.

As used herein, the term “number” shall mean one or an integer greaterthan one (i.e., a plurality).

As used herein, a “coupling assembly” includes two or more couplings orcoupling components. The components of a coupling or coupling assemblyare generally not part of the same element or other component. As such,the components of a “coupling assembly” may not be described at the sametime in the following description.

As used herein, a “coupling” or “coupling component(s)” is one or morecomponent(s) of a coupling assembly. That is, a coupling assemblyincludes at least two components that are structured to be coupledtogether. It is understood that the components of a coupling assemblyare compatible with each other. For example, in a coupling assembly, ifone coupling component is a snap socket, the other coupling component isa snap plug, or, if one coupling component is a bolt, then the othercoupling component is a nut.

As used herein, “associated” means that the elements are part of thesame assembly and/or operate together, or, act upon/with each other insome manner. For example, an automobile has four tires and four hubcaps. While all the elements are coupled as part of the automobile, itis understood that each hubcap is “associated” with a specific tire.

As used herein, “correspond” indicates that two structural componentsare sized and shaped to be similar to each other and may be coupled witha minimum amount of friction. Thus, an opening which “corresponds” to amember is sized slightly larger than the member so that the member maypass through the opening with a minimum amount of friction. Thisdefinition is modified if the two components are said to fit “snugly”together or “snuggly correspond.” In that situation, the differencebetween the size of the components is even smaller whereby the amount offriction increases. If the element defining the opening and/or thecomponent inserted into the opening are made from a deformable orcompressible material, the opening may even be slightly smaller than thecomponent being inserted into the opening. This definition is furthermodified if the two components are said to “substantially correspond.”“Substantially correspond” means that the size of the opening is veryclose to the size of the element inserted therein; that is, not so closeas to cause substantial friction, as with a snug fit, but with morecontact and friction than a “corresponding fit,” i.e., a “slightlylarger” fit. Further, as used herein, “loosely correspond” means that aslot or opening is sized to be larger than an element disposed therein.This means that the increased size of the slot or opening is intentionaland is more than a manufacturing tolerance. Further, with regard to asurface formed by two or more elements, a “corresponding” shape meansthat surface features, e.g. curvature, are similar.

As used herein, “structured to [verb]” means that the identified elementor assembly has a structure that is shaped, sized, disposed, coupledand/or configured to perform the identified verb. For example, a memberthat is “structured to move” is movably coupled to another element andincludes elements that cause the member to move or the member isotherwise configured to move in response to other elements orassemblies. As such, as used herein, “structured to [verb or “be an[X]”]” recites structure and not function. Further, as used herein,“structured to [verb or “be an [X]”]” means that the identified elementor assembly is intended to, and is designed to, perform the identifiedverb or to be an [X]. Thus, an element that is only possibly “capable”of performing the identified verb but which is not intended to, and isnot designed to, perform the identified verb is not “structured to [verbor “be an [X]”].”

As used herein, “at” means on or near.

As used herein, “cantilever” means a projecting beam or other horizontalmember supported at one or more points.

As used herein, a “tension member” is a construct that has a maximumlength when exposed to tension, but is otherwise substantially flexible,such as, but not limited to, a chain or a cable.

As shown in FIGS. 2-7, a can bodymaker 10 is structured to convert a cup2 (FIG. 2) into a can body 3 (FIG. 2). As described below, the cup 2,the ram body 50, the passage through the die pack 16, and other elementsare assumed to have a substantially circular cross-section. It isunderstood, however, that the cup 2, as well as the resulting can body 3and elements that interact with the cup 2 or can body 3, may have ashape other than substantially circular. A cup 2 has a bottom member 4with a depending sidewall 5 defining a substantially enclosed space(none shown). The end of the cup bottom member 4 is open.

The can bodymaker 10 includes a housing assembly 11, a reciprocating ramassembly 12, a drive mechanism 14, a die pack 16, a redraw assembly 18and a cup feeder 20. Each of the elements identified above are coupledto the housing assembly 11. In an exemplary embodiment, the drivemechanism 14 includes a crank assembly 30 including a reciprocatingcrank arm 32. As is known, in each cycle the cup feeder 20 positions acup 2 in front of the die pack 16 with the open end facing the ramassembly 12. The die pack 16 defines a passage 17 through a number ofdies (not shown). When the cup 2 is in position in front of the die pack16, a redraw sleeve 40 biases the cup 2 against a redraw die 42. As isknown, the drive mechanism 14 drives the redraw sleeve 40, e.g., via anumber of secondary crank arms 36 (FIG. 5), and is timed so that theredraw sleeve 40 advances just before the ram assembly 12 advances. Inan exemplary embodiment, the housing assembly 11 does not include a sealassembly for the ram body 50. That is, as the ram is not lubricated, theram body 50 does not extend through a seal assembly structured tocollect lubricant.

Generally, the ram assembly 12 includes an elongated, substantiallycircular, ram body 50 with a proximal end 52, a distal end 54, and alongitudinal axis 56. The ram body distal end 54 includes a punch 58.The ram body proximal end 52 is coupled to the drive mechanism 14. Thedrive mechanism 14 provides a reciprocal motion to the ram body 50causing the ram body 50 to move back and forth generally along itslongitudinal axis 56. That is, the ram body 50 is structured toreciprocate between a retracted, first position and a forward, secondposition over a selected path of travel. In the first, retractedposition, the ram body 50 is spaced from the die pack 16. In the second,extended position, the ram body 50 extends through the die pack 16.Thus, the reciprocating ram assembly 12 advances forward (to the left asshown) passing through the redraw sleeve 40 and engaging the cup 2. Thecup 2 is moved through the redraw die 42 and a number of ironing dies(not shown) within the die pack 16. The cup 2 is converted into a canbody 3 within the die pack 16 and then removed therefrom. It isunderstood that, as used herein, a “cycle” means the cycle of the ramassembly 12 which begins with the ram assembly 12 in the first,retracted position.

Thus, as the punch 58 carrying the can body 3 passes through the diepack 16, the can body 3 is deformed and, more specifically, the can body3 becomes elongated while the sidewall 5 becomes thinner. At the end ofthe forming stroke, a dome may be formed in the can bottom member 4 byknown methods. Further, at the start of the return stroke, the can body3 is ejected from the punch 58 by any known method or device such as,but not limited to a stripper device or delivering a compressed gas tothe inner side of the can body 3. At the start of the next formingstroke a new cup 2 is disposed over the end of the punch 58.

As shown in FIGS. 5-9, the ram assembly 12, in an exemplary embodiment,also includes an outboard guide bearing assembly 60. In a firstexemplary embodiment, the outboard guide bearing assembly 60 includes acarriage assembly 62 and a number of elongated journals 64. In oneembodiment, not shown, there is a single journal 64 disposed verticallybelow, and aligned with, i.e., parallel to but spaced from, the rainbody 50. In the embodiment shown, there are two journals 64, a firstjournal 66 and a second journal 68, that are generally horizontallyaligned with, i.e., in the same general horizontal plane as, the rambody 50. In an exemplary embodiment, the first and second journals 66,68 are slightly longer than the stroke length of the ram assembly 12 andare coupled to the bodymaker housing assembly 11.

The carriage assembly 62, for the embodiment with two journals 66, 68,includes a generally rectangular body 70 that includes a rain coupling72, a crank coupling 74, and which defines a number of journal passages80. In an exemplary embodiment, the ram coupling 72 is structured tosupport the ram body 50 in a substantially horizontal orientation. Thecrank coupling 74, in an exemplary embodiment, is a substantiallycircular bearing 76 that is structured to extend through a substantiallycircular opening (not shown) on the crank arm 32.

In an exemplary embodiment, the number of journal passages 80 includes afirst pair of substantially aligned journal passages 82 and a secondpair of substantially aligned journal passages 84. The journal passages80 in each pair of journal passages 82, 84, are spaced. In an exemplaryembodiment, the journal passages 80 in each pair of journal passages 82,84 are longitudinally spaced by about 8.0 to 12.0 inches, or about 10.25inches. The first journal 66 extends through the first pair ofsubstantially aligned journal passages 82, and, the second journal 68extends through the second pair of substantially aligned journalpassages 84. In an exemplary embodiment, the journal passages 80 aredisposed at each corner of the carriage assembly rectangular body 70.

The journal passages 80 in each pair of journal passages 82, 84, eachinclude a bearing assembly 90. In one embodiment, the bearing assembly90 includes a carbon fiber bearing (not shown). Such a carbon fiberbearing does not require a lubricant and does not include movingelements, such as, but not limited to, ball bearings. Thus, in oneembodiment, the bearing assembly 90 is a “static bearing assembly.” Thatis, as used herein, a “static bearing assembly” is a bearing assemblythat does not require a lubricant and does not include moving elements.

In this configuration, the carriage assembly body 70 is structured totravel generally in a plane and to reciprocate between a retracted,first position and a forward, second position. It is understood thatwhen the carriage assembly body 70 is in the first position, the rambody 50 is in its first position and that, when the carriage assemblybody 70 is in the second position, the ram body 50 is in its secondposition. Thus, the carriage assembly body 70 has an axis of motion 78that is substantially aligned with the ram body longitudinal axis 56.That is, the carriage assembly body axis of motion 78 may be paralleland spaced from, or be disposed substantially on, the ram bodylongitudinal axis 56.

In another embodiment, shown best in FIGS. 8 and 9, each bearingassembly 90 is a hydrostatic/hydrodynamic bearing assembly 100. As usedherein, a “hydrostatic/hydrodynamic bearing assembly” is either ahydrostatic bearing assembly, a hydrodynamic bearing assembly, or acombination thereof. As is known, a hydrostatic/hydrodynamic bearingassembly 100 includes a housing 102 and a bearing 104. The bearing 104is disposed in the housing 102. The bearing 104 defines a passage 80though which a journal 64 extends, as discussed. above. Thehydrostatic/hydrodynamic bearing assembly 100, i.e., the outboard guidebearing assembly 60, further includes a lubricant sump 106, a pumpassembly 108 and a plurality of conduits 110, all shown schematically.The hydrostatic/hydrodynamic bearing assembly conduits 110 includeconduits extending through the hydrostatic/hydrodynamic bearing assemblyhousing 102 and bearing 104. As is known, a lubricant, such as, but notlimited to oil, is passed through the conduits 110 and disposed betweenthe bearing surface and the journal 64. Alternatively, bearing 104linear motion rotation draws the fluid onto the inner surface of thebearing 104, forming a lubricating wedge or fluid lift under or aroundthe journal 64.

Because the hydrostatic/hydrodynamic bearing assemblies 100 are, in anexemplary embodiment, separate from the ram body 50, cross contaminationcooling liquid and the hydrostatic/hydrodynamic bearing assemblylubricant is greatly minimized. Thus, in an exemplary embodiment, theoutboard guide bearing assembly 60 does not include a seal assembly thatcollects the lubricant and returns the lubricant to the lubricant sump106 or a filter assembly. Rather, a portion of the housing assembly 11,i.e., the portion below the outboard guide bearing assembly 60, issubstantially hollow and defines an enclosed space that acts as the sump106. In this configuration, lubricant from the journals 64 falls intothe sump 106. Further, unlike a ram body 50, the journals 64 are notheated to the point where a cooling fluid is required. Thus, there is nocooling assembly associated with the journals 64 and/or thehydrostatic/hydrodynamic bearing assembly 100. Nor is there a filterassembly associated with the journals 64 and/or thehydrostatic/hydrodynamic bearing assembly 100 as there is no need toseparate the lubricant from a cooling fluid.

In an exemplary embodiment, when assembled, the first journal 66 andsecond journal 68, are horizontally aligned, i.e., in the same generalhorizontal plane, as noted above. Further, the first journal 66 andsecond journal 68 extend through the two pair of journal passages 82,84. Thus, the carriage assembly body 70 is structured to travel in agenerally horizontal plane. Further, the ram body 50 is also, in anexemplary embodiment, coupled to, directly coupled to, or fixed to thecarriage assembly ram coupling 72. More specifically, the ram bodyproximal end 52 is coupled to, directly coupled to, or fixed to thecarriage assembly ram coupling 72. Further, in an exemplary embodiment,the ram body 50 is disposed in the horizontal plane defined by the firstjournal 66 and second journal 68. The ram body 50, as well as thecarriage assembly body 70, travel, and more specifically reciprocate, ina direction substantially aligned with the ram body longitudinal axis56. Thus, the carriage assembly ram coupling 72 is structured to supportthe ram body 50 substantially in the plane of travel.

Utilizing an outboard guide bearing assembly 60 allows the can bodymaker10 to operate without a seal assembly disposed about the ram body 50, asnoted above. Further, the ram body 50 does not pass through ahydrostatic/hydrodynamic bearing assembly or ram guide. Thus, unlikeknown ram bodies that must have a sufficient length to pass throughthese elements/assemblies, as well as the die pack 16, the ram body 50of the exemplary embodiment only needs to have a sufficient length topass through the die pack 16. This reduction in the length of the rambody 50 reduces the amount of ram droop and thereby reduces the wear andtear on the ram body 50 and the die pack 16. In an exemplary embodiment,the ram body 50 has a length between about 30.0 inches and 32.0 inches,or in another embodiment, a length of about 31.0 inches. That is, thechange in size ameliorates the known disadvantages of the known art.

Known ram bodies 50 exist in a number of sizes. The dimensionsidentified above are associated with one exemplary embodiment, e.g., aram body 50 sized for standard 12 fluid ounce cans. In the prior art,such a ram body had a length of between about 50 inches to 52 incheswhen using a 24 inch stroke. Accordingly, it is understood that thedisclosed concept allows for a reduction in the length of a ram body ofabout 40% plus or minus about an inch. Other known ram body lengthsinclude, 45.387 inches, 50.0 inches, 51.0 inches, and 57.0 inches, allplus or minus about an inch. Thus, the disclosed concept also providesfor ram bodies (not shown) having lengths of about 27.0 inches, 30.0inches, and 34.2 inches, all plus or minus about an inch. Alternatively,and stated broadly, a ram body 50 with a reduced length has a lengthbetween about 26.0 inches and 36.0 inches, all of which are shorter thanknown ram body lengths. That is, as used herein, a “reduced length rambody” has a length of between about 26.0 inches and 36.0 inches.

In another exemplary embodiment, shown in FIGS. 11-13 and 19-20, anoutboard guide bearing assembly 160 includes a carriage assembly 162including a body 170 with a ram coupling 172, a crank coupling 174, anda number of guide bearing assemblies 180, as well as a pump assembly 108and a plurality of conduits 110 as before. As before, the carriageassembly guide bearing assemblies 180 are separated from the ram body50. That is, as before, the carriage assembly body 170 is, in anexemplary embodiment, generally rectangular and includes a forward,axial surface 171, a first lateral surface 173, and a second lateralsurface 175. The ram coupling 172 is disposed on the carriage assemblybody forward, axial surface 171, i.e., the forward surface through whichthe axis of motion passes. The ram coupling 172 is structured to supportthe ram body 50 in a substantially horizontal orientation. As before,the carriage assembly body 170 is structured to travel generally in aplane and to reciprocate between a retracted, first position and aforward, second position.

The carriage assembly guide bearing assemblies 180, in an exemplaryembodiment, include two carriage assembly guide bearing assemblies 180;a carriage assembly first guide bearing assembly 180A, and a carriageassembly second guide bearing assembly 180B. In an exemplary embodiment,the carriage assembly first guide bearing assembly 180A is disposed on,and coupled to, the carriage assembly body first lateral surface 173,and, the carriage assembly second guide bearing assembly 180B isdisposed on, and coupled to, the carriage assembly body second lateralsurface 175. It is further understood that elements of the carriageassembly first and second guide bearing assemblies 180A, 180B are alsocoupled to the bodymaker housing assembly 11, as described below. It isnoted that, with the ram body 50 coupled to the carriage assembly bodyforward, axial surface 171 and the carriage assembly first and secondguide bearing assemblies 180A, 180B coupled to the carriage assemblybody first and second lateral surfaces 173, 175, the carriage assemblyguide bearing assemblies 180A, 180B are separated from the ram body 50.

As the carriage assembly first and second guide bearing assemblies 180A,180B are substantially similar, only one will be described. It isunderstood, however, that each carriage assembly guide bearing assembly180A, 180B includes the elements described hereinafter and such elementsassociated with the carriage assembly first guide bearing assembly 180Aare identified by the reference letter “A” and elements associated withthe carriage assembly second guide bearing assembly 180B are identifiedby the reference letter “B,” even when that indication is not providedwith the initial description of the elements. Further, hereinafter, thenames of components of each carriage assembly guide bearing assembly 180may be shortened to “first [X]” and “second [X].” For example, in anexemplary embodiment, the carriage assembly first and second guidebearing assemblies 180A, 180B each include a saddle 186, describedbelow. A saddle 186 may thereafter be identified as a “first saddle186A” or a “second saddle 186B”, it is understood that the term “first”and “second” identify the carriage assembly guide bearing assembly 180with which the component is associated.

In an exemplary embodiment, a carriage assembly guide bearing assembly180 includes a first component 182 and a second component 184. Thecarriage assembly guide bearing assembly first component 182 is a saddle186 and the carriage assembly guide bearing assembly second component184 is a journal channel 188. That is, as used herein, a journal channel188 is a channel that defines a path of travel, similar to the journals66, 68 described above. Further, as used herein, a “saddle” is aconstruct sized to substantially correspond to the associated channel188. That is, the saddle 186 has a similar, but slightly smaller,cross-sectional shape as the channel 188, and, a reduced longitudinaldimension. In this configuration, the saddle 186 is structured to travelthrough the channel 188. In an exemplary embodiment, each saddle 186 isunitary with the carriage assembly body 170.

In an exemplary embodiment, the journal channel 188 is formed of anumber of generally planar surfaces forming a generally square C-shapedchannel. That is, the channel 188 has a generally rectangularcross-section. Accordingly, the corresponding saddle 186 has a generallyrectangular cross-section as well. Further, as shown in FIG. 12, in anexemplary embodiment, saddle 186 is a generally parallelepipedconstruct. In an alternate embodiment, not shown, the channel 188 andthe saddle 186 have a trapezoidal cross-sectional shape.

Further, in an exemplary embodiment, the carriage assembly guide bearingassembly 180 is a hydrostatic/hydrodynamic bearing assembly. In thisembodiment, the bearing assembly first component 182 is structured to becoupled to, and in fluid communication with, a lubricant sump 106. Thatis, the saddle 186 includes a number of fluid ports 190 that are coupledto, and in fluid communication with, the lubricant sump 106. As before,a plurality of conduits 110 provide fluid communication for a lubricantand allow the lubricant to be pumped by pump assembly 108 from the sump106 through the fluid ports 190. The plurality of conduits 110, in anexemplary embodiment, pass through the carriage assembly body 170. Inthis configuration, a layer of lubricant is disposed between thecarriage assembly guide bearing assembly first component 182 and thecarriage assembly guide bearing assembly second component 184.

In an exemplary embodiment, the carriage assembly guide bearing assemblysecond component 184 includes a gib assembly 192. A gib assembly 192includes a number, typically two, generally parallel planar members (notshown) coupled by spaced, adjustable coupling components, such as butnot limited to, threaded rods (not shown).

The relative spacing and angle of the planar members can be adjusted byactuating the adjustable coupling components. For example, if a journalchannel 188 is a generally square C-shaped channel having threegenerally planar surfaces, each planar surface may be formed by a gibassembly 192. That is, one of each gib assembly 192 planar members formseach of the square C-shaped channel planar surface. In thisconfiguration, the characteristics, e.g., alignment of the channelsurfaces or cross-sectional area of the journal channel 188, can beadjusted.

In an exemplary embodiment, the carriage assembly guide bearing assembly180 is structured to orient the ram body 50, or the punch 58, with thepassage through the die pack 16. To be “structured to orient the rambody,” with the longitudinal axis of the die pack passage 17 as usedherein, means to be structured to alter the orientation of a ram body,or a punch, in a manner intended to position the longitudinal axis ofthe ram body 50 in line with the axis of the die pack 16 whereby the rambody 50 does not need to be supported by a guide bearing. Orienting theram body 50 reduces the misalignment of the punch 58 and the die pack 16and dampens the “wobble,” described above. That is, a prior art bearingassembly, including a hydrostatic/hydrodynamic bearing assembly, has aneffect on the orientation of the associated ram body 50 or punch 58, butother assemblies, such as but not limited to, a guide assemblysubstantially controlled the orientation of the ram body 50 or punch 58.That is, a hydrostatic/hydrodynamic bearing assembly 100 has acompensating effect. For example, on a carriage assembly body 170including a hydrostatic/hydrodynamic bearing assembly 100, any offset inthe carriage assembly 62 relative to the channels 188 will narrow thegap between the carriage assembly guide bearing assembly first component182 and the carriage assembly guide bearing assembly second component184 at one location and increase the gap at another location. Thischange in the gap changes the fluid pressure at those locations, i.e.,increasing the pressure where the gap is narrowed and decreasing thepressure where the gap is increased. This, in turn, causes the carriageassembly 62 to be reoriented so as to balance the pressure. Thecompensating effect of hydrostatic/hydrodynamic bearing assemblies ofthe prior art, wherein the pads are disposed adjacent each other, asshown in FIG. 1, is not, as used herein, “structured to orient the rambody.”

Stated alternately, various characteristics, such as but not limited tomanufacturing tolerances, of a prior art bearing assembly, including ahydrostatic/hydrodynamic bearing assembly and the location of thehydrostatic/hydrodynamic fluid bearing assemblies immediately adjacenteach other, allowed the ram body or punch to wobble relative to thebodymaker housing assembly; thus prior art hydrostatic/hydrodynamicfluid bearing assemblies required a ram guide. To be “structured toorient the ram body,” as used herein, means that the guide bearingassembly substantially controls the orientation of the ram body 50 orpunch 58. To substantially control the orientation of the ram body 50 orpunch 58, a bearing assembly, including a guide bearing assembly 180,must control the orientation of the ram body 50 or the punch 58 in anintended manner as a result of more than the compensating effectdiscussed above. To “control the orientation of the ram body or punch”(50, 58) as used herein, means that the hydrostatic/hydrodynamic bearingassembly 100 includes the following characteristics: (1) the fluidproducing elements of the carriage assembly guide bearing assemblies 180are “sufficiently spaced” so as to alter the orientation of a ram body50, or a punch 58, in a manner intended to position the longitudinalaxis of the ram body 50 to move over a selected path of travel, and (2)the carriage assembly guide bearing assemblies 180 “produce asufficient, but reasonable, amount of fluid to establish an aligningfluid bearing stiffness.” As discussed below, and in an exemplaryembodiment, the fluid producing elements of the carriage assembly guidebearing assemblies 180 are thrust pad assemblies 400.

As used herein, “produce” means to pass fluid through the pump assembly108, the plurality of conduits 110, and the carriage assembly guidehearing assemblies 180. That is, “produce” does not mean “create.”Further, “produce” means to pass fluid through the pump assembly 108,the plurality of conduits 110, and the carriage assembly guide bearingassemblies 180 at a sufficient volume of bearing fluid so that thebearing fluid acts to stiffen, i.e., make more rigid, the guide bearingassembly 180. Thus, with regard to “produc[ing] a sufficient, butreasonable, amount of fluid to establish an aligning fluid bearingstiffness,” it is understood that the fluid disposed between the guidebearing assembly first component 182 and second component 184 is at asufficient pressure to effectively eliminate the wobble of the ram body50 or punch 58 relative to the bodymaker housing assembly 11 and toalign the longitudinal axis of the ram body 50 with the axis of the diepack 16. This is not possible with hydrostatic/hydrodynamic fluidbearing assemblies 100 in every configuration. By way of an impossibleexample, if a hydrostatic/hydrodynamic bearing assembly 100 including apump and the hydrostatic/hydrodynamic fluid bearing assemblies 100,shown in FIG. 1 (and which are immediately adjacent each other), werestructured to provide a nearly infinite fluid flow rate, then such ahydrostatic/hydrodynamic bearing assembly could produce an amount offluid to establish an aligning fluid bearing stiffness. A nearlyinfinite fluid flow rate, however, is not “reasonable” as it isunderstood that the fluid flow characteristics of a pump assembly 108,any conduits 110, and the hydrostatic/hydrodynamic fluid bearingassemblies 100 are limited by physics and present technology.Accordingly, to “produce a sufficient, but reasonable, amount of fluidto establish an aligning fluid bearing stiffness” as used herein meansthat the fluid in the bearing assembly is at a sufficient pressure toeffectively eliminate the wobble of the ram body 50, or punch 58,relative to the bodymaker housing assembly 11 using components known tothose of skill in the art. Thus, a hydrostatic/hydrodynamic bearingassembly that is ostensibly “capable” of “establishing an aligning fluidbearing stiffness” if given, for example, a nearly infinite fluid flowrate is not “structured to orient the ram body” because such animaginary hydrostatic/hydrodynamic bearing assembly does not “produce asufficient, but reasonable, amount of fluid to establish an aligningfluid bearing stiffness.” That is, an infinite fluid flow is not“reasonable.” Further, and to be clear, hydrostatic/hydrodynamic fluidbearing assemblies 100 which are immediately adjacent each other, asshown in FIG. 1, as used herein, cannot “produce a sufficient, butreasonable, amount of fluid to establish an aligning fluid bearingstiffness.”

Further, “sufficiently spaced” as used herein with respect to carriageassembly guide bearing assemblies 180, means that the carriage assemblyguide bearing assemblies 180 are not immediately adjacent each other. Itis understood that the ability of the guide bearing assemblies 180 toorient the ram body 50, or the punch 58, with the passage through thedie pack 16 is a function of the fluid pressure between the carriageassembly guide bearing assembly first component 182 and the carriageassembly guide bearing assembly second component 184, as discussedabove, as well as the spacing of the carriage assembly guide bearingassemblies 180, and the distance of the guide bearing assemblies 180from the center of gravity of the ram assembly 12. Other characteristicsof the ram assembly 12 also affect the orientation, but to a lesser and,as used herein, a negligible extent. As shown in FIGS. 22A-22C, thecenter of gravity of the ram assembly 12 is located at the interface ofthe ram body 50 and the carriage assembly body 170 at about the ram bodylongitudinal axis 56. It is understood that the further a carriageassembly guide bearing assembly 180 is spaced from the center of gravityof the ram assembly 12 the greater affect the fluid passing through athrust pad assembly 400, discussed below, has on the position of the rambody 50. That is, the further a thrust pad assembly 400 is from thecenter of gravity of the ram assembly 12, the greater the lever arm.Thus, to “produce a sufficient, but reasonable, amount of fluid toestablish an aligning fluid bearing stiffness” also depends upon thelocation of the thrust pad assemblies 400 relative to the center ofgravity of the ram assembly 12. Further, as used herein, to be“sufficiently spaced” means that the thrust pad assemblies 400 arespaced so that, for the amount of fluid produced by the thrust padassemblies 400, the thrust pad assemblies 400, i.e., the carriageassembly guide bearing assemblies 180, are structured to alter theorientation of a ram body 50, or a punch 58, in a manner intended toposition the longitudinal axis of the ram body 50 to move over aselected path of travel. Thus, with “sufficiently spaced” thrust padassemblies 400, a known pump assembly 108 and a known conduits 110 can“produce a sufficient, but reasonable, amount of fluid to establish analigning fluid bearing stiffness.” Thus, having “sufficiently spaced”thrust pad assemblies 400 solves the stated problem relating to the“wobble” noted above.

For example, and in general terms, with a relatively short ram assembly12, lesser force is required to orient the ram body 50, or the punch 58,with the passage through the die pack 16. Thus, the carriage assemblyguide bearing assemblies 180 may be moderately spaced and the outboardguide bearing assembly 160 is structured to produce a moderate amount ofguide fluid. Moreover, the amount of fluid produced at a thrust padassembly 400 relatively near the center of gravity of the ram assembly12 is greater than the amount of fluid produced at a thrust pad assembly400 relatively far from the center of gravity of the ram assembly 12.

If, with the same relatively short ram assembly 12, the spacing of thecarriage assembly guide bearing assemblies 180 was increased, i.e., ifthe rear thrust pad assembly 400 was even further from the center ofgravity of the ram assembly 12, the outboard guide bearing assembly 160is structured to produce a lesser amount of guide fluid. Conversely,with a relatively long ram assembly 12, the carriage assembly guidebearing assemblies 180 would need to have a greater spacing and theoutboard guide bearing assembly 160 would need to produce a greateramount of guide fluid when compared to the outboard guide bearingassembly 160 supporting the relatively short ram assembly 12.

Thus, a guide bearing assembly 180 that is “structured to orient the rambody 50” is a guide bearing assembly 180 that “produce[s] a sufficientamount of fluid to establish an aligning fluid bearing stiffness,” and,wherein the fluid producing elements of the carriage assembly guidebearing assemblies 180 are “sufficiently spaced” from each other. Thus,the reverse is also true, i.e., a guide bearing assembly 180 that“produce[s] a sufficient amount of fluid to establish an aligning fluidbearing stiffness” and wherein the fluid producing elements of thecarriage assembly guide bearing assemblies 180 are “sufficiently spaced”is “structured to orient the ram body 50.”

Further, as noted above, to be “structured to [verb or ‘be an [X]’]” theconstruct must be intended to, and is designed to, perform theidentified verb or to be an [X]. Thus, as used herein, a lubricatedbearing assembly that merely uses a lubricating fluid is not “structuredto orient the ram body 50” unless specifically described as doing so.Stated alternately, a prior art bearing assembly that is possiblycapable of altering the orientation of a ram body 50, or a punch 58, inan intended manner is not, as used herein, “structured to orient the rambody” and does not “produce a sufficient amount of fluid to establish analigning fluid bearing stiffness” and does not include fluid producingelements of the carriage assembly guide bearing assemblies 180 that are“sufficiently spaced.” To be “structured to orient the ram body 50” and“produce a sufficient amount of fluid to establish an aligning fluidbearing stiffness,” and which includes fluid producing elements of thecarriage assembly guide bearing assemblies 180 that are “sufficientlyspaced,” a guide bearing assembly 180 must be described as being able toorient the ram body 50 or must be designed to or be shown tointentionally orient the ram body 50.

It is again noted that the carriage assembly first and second guidebearing assemblies 180A, 180B are substantially similar, only one willbe described. It is understood, however, that each carriage assemblyguide bearing assembly 180A, 180B includes the elements describedhereinafter. In an exemplary embodiment, shown in FIGS. 19-21, eachsaddle 186 includes a number of thrust pad assemblies 400. As describedbelow, a unitary body component may extend over separate thrust padassemblies 400; the thrust pad assemblies 400, however, are stillseparate and distinct assemblies. In an exemplary embodiment, the saddle186 has a generally rectangular cross-section, i.e., a parallelepipedcross-section; thus, each saddle 186 has an upper surface 181, an outerlateral surface 183, and a lower surface 185. In this configuration,each thrust pad assembly 400 includes an upper pad portion 402, alateral pad portion 404, and a lower pad portion 406. The upper padportion 402 is disposed on the saddle upper surface 181. The lateral padportion 404 is disposed on the saddle outer lateral surface 183. Thelower pad portion 406 is disposed on the saddle lower surface 185.

Each pad portion 402, 404, 406 is substantially similar and only onewill be described. A pad portion 402, 404, 406 includes a generallyplanar pad body 410. Each pad portion body 410, in an exemplaryembodiment, defines a recessed slot 412. Within the pad portion bodyslot 412 is a fluid passage 414 and a number of coupling passages (notshown). Each pad portion body fluid passage 414 is structured, i.e.,positioned, to align with a fluid distribution assembly passage 452,described below.

In an exemplary embodiment, each saddle 186 includes a forward thrustpad assembly 400′, at least one medial thrust pad assembly 400″, and arear thrust pad assembly 400″. It is noted that the inclusion of atleast one medial thrust pad assembly 400″ in excess of the forwardthrust pad assembly 400′ and the rear thrust pad assembly 400′″, i.e.,each additional medial thrust pad assembly 400″, provides for additionalorienting forces and a better ability to provide a resultingcounteracting moment to any offsetting forces, as described above.Moreover, the addition of at least one medial thrust pad assembly 400″means that the burden of “produc[ing] a sufficient, but reasonable,amount of fluid to establish an aligning fluid bearing stiffness” isdivided among additional thrust pad assemblies. That is, currenttechnology pump assemblies 108 and conduits 110 are insufficient to“produce a sufficient, but reasonable, amount of fluid to establish analigning fluid bearing stiffness” in insufficiently spaced thrust padassemblies; that is, for example, the required fluid pressure isunobtainable or would burst the conduits. By including at least onemedial thrust pad assembly 400″, this required fluid pressure is reducedso that current technology pump assemblies 108 and conduits 110 aresufficient to “produce a sufficient, but reasonable, amount of fluid toestablish an aligning fluid bearing stiffness.” Thus, the inclusion ofat least one medial thrust pad assembly 400″ solves the stated problemrelating to the “wobble” noted above. It is understood that three thrustpad assemblies 400′, 400″, 400′″ are exemplary only and each saddle 186may include any number of thrust pads so long as that number is greaterthan one and so long as the trust pads 400 are “sufficiently spaced”from each other as defined above. As shown, and in an exemplaryembodiment, there is one medial thrust pad assembly 400″. Hereinafter,the number of “′” marks indicate components of the separate padassemblies 400′, 400″, 400′″. As shown in FIG. 19, in each forwardthrust pad assembly 400′ and medial thrust pad assembly 400″, the upperpad portions 402′, 402″, lateral pad portions 404′, 404″, and lower padportions 406′, 406″ are generally aligned. That is, for example, theforward edge and rear edge of each pad portion body 410 in each forwardthrust pad assembly 400′ and medial thrust pad assembly 400″ aredisposed generally in the same plane. In the rear thrust pad assembly400′″, the upper pad portion 402′″ and lower pad portion 406′″ arelongitudinally offset from the lateral pad portion 404′″. In thisconfiguration, the pin 33 coupling the crank assembly crank arm 32 tothe carriage assembly body 170 is disposed between the upper pad portion402′″ and lower pad portion 406′″.

In an exemplary embodiment, the forward thrust pad assembly 400′, the atleast one medial thrust pad assembly 400″, and the rear thrust padassembly 400′″ share a number of unitary pad members 430, 432, 434. Thatis, each carriage assembly guide bearing assembly 180 includes a unitaryupper pad member 430, a unitary lateral pad member 432, and a unitarylower pad member 434. The unitary upper pad member 430 includes anelongated, generally planar unitary body 448 that defines the forwardthrust pad assembly upper pad portion 402′, the medial thrust padassembly upper pad portion 402″, and the rear thrust pad assembly upperpad portion 402′″. That is, the generally planar upper pad member 430includes recesses, i.e., thinner portions of the pad member body 448thereby defining the thicker portions as the various pad portion bodies410. Similarly, the unitary lateral pad member 432 defines the forwardthrust pad assembly lateral pad portion 404′, the medial thrust padassembly lateral pad portion 404″, and the rear thrust pad assemblylateral pad portion 404′″, and the unitary lower pad member 434 definesthe forward thrust pad assembly lower pad portion 406′, the medialthrust pad assembly lower pad portion 406″, and the rear thrust padassembly lower pad portion 406′″.

In an exemplary embodiment, each carriage assembly guide bearingassembly 180 includes a fluid distribution assembly 450 structured toprovide a balanced fluid flow to associated saddle thrust pad assemblies400. Thus, each saddle 186, i.e., each fluid distribution assembly 450,includes a number of passages 452. Each fluid distribution assemblypassage 452 is structured to be coupled to, and in fluid communicationwith a pad body fluid passage 414 as well as the lubricant sump 106. Inthis configuration, lubricant is transferred to the carriage assemblyguide bearing assembly 180.

Further, the fluid distribution assembly passages 452 are structured to“provide a balanced fluid flow” to associated saddle thrust padassemblies 400. As used herein, to “provide a balanced fluid flow” meansthat the fluid distribution assembly passages 452 provide sufficientfluid flow to the associated portions 402, 404, 406 so that the carriageassembly guide bearing assembly 180 “produce[s] a sufficient amount offluid to establish an aligning fluid bearing stiffness,” as definedabove, and to produce fluid at a rate so that the fluid pressure at eachfluid port 190 is generally equivalent. Thus, it is understood that theconfiguration of the fluid distribution assembly passages 452 dependsupon the weight and configuration of the bodymaker 10 and the ramassembly 12. It is noted that to be structured to “provide a balancedfluid flow” a fluid distribution assembly must be described as beingable to “provide a balanced fluid flow” or must be designed or shown tointentionally “provide a balanced fluid flow.” That is, a fluiddistribution assembly that merely provides a fluid flow does not“provide a balanced fluid flow” as used herein, unless the fluiddistribution assembly is described as being able to “provide a balancedfluid flow” or is designed to or is shown to intentionally “provide abalanced fluid flow.”

Further, a number of the fluid distribution assembly fluid passages 452are selectively closable. For example, a number of the individual fluiddistribution assembly fluid passages 452 are structured have a plug (notshown) installed therein. The plug seals the individual fluiddistribution assembly fluid passage 452. In an exemplary embodiment, theplug is disposed on the carriage assembly body 170 at the openingstructured to interface with the conduit 110 to the sump 106.Alternatively, a plug may be disposed in a pad body fluid passage 414.In another embodiment, not shown, a number of the fluid distributionassembly fluid passages 452 include a valve assembly (not shown) thatmoves between an open position and a closed position.

In this configuration, the first and second saddles 186A, 186B arestructured to produce a sufficient amount of fluid to establish analigning fluid bearing stiffness. That is, as used herein, the first andsecond saddles 186A, 186B with a forward thrust pad assembly 400′, atleast one medial thrust pad assembly 400″, and a rear thrust padassembly 400′″, wherein the thrust pad assemblies 400′, 400″, 400′″ arecoupled to, and in fluid communication with, a fluid distributionassembly passages 452 structured to “provide a balanced fluid flow” andto produce a sufficient amount of fluid to establish an aligning fluidbearing stiffness.

In this embodiment, the housing assembly 11 may, and as shown does,include a seal assembly 196 for the ram body 50. That is, the sealassembly 196 includes two cup seals, not shown, as is known. That is,one cup seal is structured to remove coolant from the ram body 50 as theram body travels to the second position to the first position, and, theother cup seal is structured to remove lubricant from the ram body 50 asthe ram body 50 travels from the first position to the second position.It is noted that the seal assembly 196 is not a bearing assembly anddoes not support the ram body 50 and, therefore, does not change the“cantilever length” of the ram body 50, as discussed below.

In this embodiment, unlike known ram bodies that must have a sufficientlength to pass through a bearing assembly, the ram body 50 of thisexemplary embodiment only needs to have a sufficient length to passthrough the seal assembly 196 and the die pack 16. This reduction in thelength of the ram body 50 reduces the amount of ram droop and therebyreduces the wear and tear on the ram body 50 and the die pack 16. In anexemplary embodiment, the ram body 50 has a length of between about 33.0inches to about 36.0 inches, or about 34.5 inches. That is, the changein size ameliorates the disadvantages of the known art.

With either embodiment of the outboard guide bearing assembly 60, 160,the ram body proximal end 52 is coupled to, directly coupled to, orfixed to the carriage assembly ram coupling 72 and the ram body 50extends therefrom, the ram body 50 is a cantilever member 120, 220(FIGS. 8 and 13). It is noted that the assemblies, such as but notlimited to an air blade 44 and a mechanical stripper 46, to the right ofthe redraw sleeve 40 as shown in FIG. 3, does not support the ram body50.

Further, a cantilever member 120 has a “cantilever length” which is thelength of the cantilever member beyond the support that is closest tothe unsupported end. As noted above, in the prior art wherein a ram body50 moved through a bearing assembly 60, the cantilever length of theprior art ram body had a dynamic cantilever length. That is, thecantilever length depended upon the length of the ram body 50 extendingthrough the bearing assembly 60. As the ram body 50 of the exemplaryembodiment does not extend through a bearing assembly 60, the cantileverlength of the cantilever member 120 remains constant during thereciprocal motion of the carriage assembly 62.

In another exemplary embodiment, shown in FIGS. 10, 10A, and 10B, theram assembly 12 includes an elongated, substantially circular, generallyhollow ram body 50A. As before, the ram body 50A includes a proximal end52, a distal end 54, and a longitudinal axis 56, as well as a medialportion 59. In an exemplary embodiment, and at the ram body medialportion 59, the inner surface of the hollow ram body 50A includes aninwardly extending flange 130. In this exemplary embodiment, the rambody flange 130 is the boundary between the ram body distal end 54 andthe ram body medial portion 59.

The punch 58 is disposed on the ram body distal end 54 beyond theinwardly extending flange 130. That is, the ram body distal end 54 has areduced radius relative to the ram body proximal end 52 and ram bodymedial portion 59. The punch 58 is generally cylindrical and includes ahollow body 57. The outer diameter of the punch body 57 is substantiallythe same as the outer diameter of the ram body medial portion 59 andproximal end 52. The punch 58 is disposed over, and coupled to, the rambody distal end 54. In this configuration, the outer transition betweenthe punch 58 and the ram body medial portion 59 is substantially smooth.In this exemplary embodiment, the ram assembly 12 also includes atension assembly 140.

The tension assembly 140 is structured to place the ram body 50A undertension and thereby reduce the ram droop. In an exemplary embodiment,the tension assembly 140 includes an elongated support member 142, aproximal coupling assembly 144, and a distal coupling assembly 146. Thesupport member 142 includes a proximal end 150, a distal end 152, and alongitudinal axis 154. The support member 142 is, in an exemplaryembodiment, one of a rigid member or a tension member. The supportmember 142 is substantially disposed within the ram body 50A.

The tension assembly proximal coupling assembly 144 is disposed at theram body proximal end 52. The tension assembly proximal couplingassembly 144 is, in an exemplary embodiment, an adjustable couplingassembly 148. That is, in an exemplary embodiment, the support memberproximal end 150 and the tension assembly proximal coupling assembly 144are threaded couplings, e.g., a threaded rod 143 and a captive nut 145,respectively. As shown, the support member proximal end 150 extendsthrough an axial passage 149 within the ram body proximal end 52. Asshown, the ram body proximal end axial passage 149 is disposed on acollar 147 that defines an inwardly extending flange.

The tension assembly distal coupling assembly 146 is disposed at one ofthe ram body medial portion 59 or ram body distal end 54. In anexemplary embodiment, the tension assembly distal coupling assembly 146is disposed at the ram body flange 130. In an exemplary embodiment, thetension assembly distal coupling assembly 146 includes a mounting 260and a mounting coupling assembly 262. That is, the mounting couplingassembly 262 includes the coupling components, described below, thatcoupled the mounting 260 to the ram body 50A. The tension assemblydistal coupling assembly mounting 260 includes a body 264 defining anaxial, first coupling assembly 266 and a radial, second couplingassembly 268. The tension assembly distal coupling assembly mountingbody 264 is otherwise sized and shaped to fit within the ram body 50A atthe ram body flange 130. The tension assembly distal coupling assemblymounting body first coupling assembly 266 includes, in an exemplaryembodiment, a threaded cavity 270. In an alternate embodiment, thecavity 270 includes radial pins and passages therefor (not shown.) Thetension assembly distal coupling assembly mounting body first couplingcomponent cavity 270 corresponds to the support member distal end 152.Thus, when the support member distal end 152 is threadably disposed inthe tension assembly distal coupling assembly mounting body firstcoupling component cavity 270 it couples the support member 142 to thetension assembly distal coupling assembly mounting body 264.

The tension assembly distal coupling assembly mounting body 264 iscoupled to the ram body 50A by the tension assembly distal couplingassembly mounting body second coupling assembly 268. In an exemplaryembodiment, the tension assembly distal coupling assembly mounting bodysecond coupling assembly 268 includes a threaded bore 290, which extendsgenerally radially, in the tension assembly distal coupling assemblymounting body 264. The tension assembly distal coupling assemblymounting body second coupling assembly 268 also includes a fastener 292and a radial passage 294 through the ram body medial portion 59 at theflange 130. The tension assembly distal coupling assembly mounting body264 is disposed within the ram body 50A at the flange 130. The tensionassembly distal coupling assembly mounting body second couplingcomponent fastener 292 is passed through the tension assembly distalcoupling assembly mounting body second coupling component radial passage294 and threaded into the tension assembly distal coupling assemblymounting body second coupling component threaded bore 290, therebycoupling, and fixing, the tension assembly distal coupling assemblymounting 260 to the ram body 50A.

The support member 142 extends between, and is coupled to, the tensionassembly proximal coupling assembly 144 and the tension assembly distalcoupling assembly 146. The support member 142 is placed under tension.The coupling of the support member distal end 152 to the tensionassembly distal coupling assembly 146 is described above. As furthernoted above, and in an exemplary embodiment, the support member proximalend 150 and the tension assembly proximal coupling assembly 144 arethreaded couplings, e.g., a threaded rod 143 and a captive nut 145,respectively. That is, the support member proximal end 150 is threaded.In this configuration, the tension in the support member 142 can beeasily adjusted. That is, the captive nut 145 is threaded onto thesupport member proximal end 150 and drawn against the ram body proximalend collar 147. The captive nut 145 is drawn against the ram bodyproximal end collar 147 creating tension in the support member 142.Thereafter, rotating the captive nut 145 on the threaded rod 143increases or decreases the tension on support member 142.

Further, in an exemplary embodiment, the support member 142 is disposedabove, and aligned with, the ram body longitudinal axis 56. That is, thesupport member longitudinal axis 154 is generally parallel to, andspaced from, the ram body longitudinal axis 56.

In another exemplary embodiment, shown in FIGS. 14 and 14A, a tensionassembly 340 is structured to be substantially enclosed. That is, inthis embodiment, the construct that couples the mounting body to the rambody 50A is not exposed on the ram body 50A outer surface. In thisconfiguration, the construct that couples the mounting body 264 to theram body 50A is not in a position that causes wear and tear on a sealassembly 196. Thus, as shown in FIG. 14, the support member 142 and thetension assembly proximal coupling assembly 144 are substantially asdescribed above. In this embodiment, however, the tension assemblydistal coupling assembly 146 is as described below.

In this exemplary embodiment, the tension assembly distal couplingassembly 146 includes a mounting 360 and a mounting coupling assembly362. That is, the mounting coupling assembly 362 includes the couplingcomponents, described below, that coupled the mounting 360 to the rambody 50A. The tension assembly distal coupling assembly mounting 360includes a body 364 having a first, distal end 363 and a second,proximal end 365 as well as defining the axial, first coupling assembly366 and a radial, second coupling assembly 368. The tension assemblydistal coupling assembly mounting body 264 is sized and shaped to fitwithin the ram body 50A and extend over the ram body flange 130. Thatis, when installed, the tension assembly distal coupling assemblymounting body distal end 363 is disposed on the distal side of theflange 130.

The tension assembly distal coupling assembly mounting body firstcoupling component 266 is disposed on the tension assembly distalcoupling assembly mounting body proximal end 365 and includes, in anexemplary embodiment, a threaded cavity 370. The tension assembly distalcoupling assembly mounting body first coupling component cavity 370corresponds to the support member distal end 252. In this exemplaryembodiment, the support member distal end 252 includes threads 374.Thus, the support member distal end 252 is threadably coupled to thetension assembly distal coupling assembly mounting body first couplingcomponent cavity 370.

The tension assembly distal coupling assembly mounting body 364 iscoupled to the ram body 50A by the tension assembly distal couplingassembly mounting body second coupling assembly 368. In an exemplaryembodiment, the tension assembly distal coupling assembly mounting bodysecond coupling assembly 368 includes a threaded bore 390, which extendsgenerally radially, in the tension assembly distal coupling assemblymounting body 364. The tension assembly distal coupling assemblymounting body second coupling assembly 368 also includes a fastener 392and a radial passage 394 through the ram body distal end 54 at alocation distal to the flange 130. The tension assembly distal couplingassembly mounting body 364 is disposed within the ram body 50A at theflange 130. The tension assembly distal coupling assembly mounting bodysecond coupling component fastener 392 is passed through the tensionassembly distal coupling assembly mounting body second couplingcomponent radial passage 394 and threaded into the tension assemblydistal coupling assembly mounting body second coupling componentthreaded bore 390, thereby coupling, and fixing, the tension assemblydistal coupling assembly mounting 260 to the ram body 50A.

It is noted that, when the ram assembly 12 is assembled, the tensionassembly distal coupling assembly 146 is disposed below/within the punch58. Stated alternately, the punch 58 covers the tension assembly distalcoupling assembly 146. Thus, in operation, as the ram body reciprocatesbetween the first and the second positions, the tension assembly distalcoupling assembly 146 is not exposed and cannot contact a seal assembly196. As used herein, a coupling assembly that is not visible fromoutside the ram body 50A is a “hidden coupling.” Thus, in thisembodiment, the tension assembly distal coupling assembly mounting bodysecond coupling assembly 368 is a hidden coupling.

While specific embodiments of the invention have been described indetail, it will be appreciated by those skilled in the art that variousmodifications and alternatives to those details could be developed inlight of the overall teachings of the disclosure. Accordingly, theparticular arrangements disclosed are meant to be illustrative only andnot limiting as to the scope of invention which is to be given the fullbreadth of the claims appended and any and all equivalents thereof.

What is claimed is:
 1. A carriage assembly guide bearing assembly for acan bodymaker, said bodymaker including an elongated ram body, a crankassembly, a housing assembly, a die pack and a carriage assembly, saiddie pack defining a passage, said carriage assembly including a bodywith a ram coupling, a crank coupling, a first lateral surface and asecond lateral surface, said crank assembly including a reciprocatingcrank arm, said crank arm coupled to said carriage assembly body crankcoupling, said ram body coupled to said carriage assembly body raincoupling, said carriage assembly guide bearing assembly comprising: anumber of guide bearing assemblies; each guide bearing assemblyincluding a first component and a second component; and wherein eachsaid carriage assembly guide bearing assembly is structured to orientsaid ram body with said die pack passage.
 2. The carriage assembly guidebearing assembly of claim 1 wherein: each said carriage assembly guidebearing assembly first component is a saddle; and each said carriageassembly guide bearing assembly second component is a journal channel.2. The carriage assembly guide bearing assembly of claim 2 wherein: eachsaid saddle includes a number of thrust pad assemblies; and each saidsaddle structured to produce a sufficient amount of fluid to establishan aligning fluid bearing stiffness.
 4. The carriage assembly guidebearing assembly of claim 3 wherein: each said saddle number of thrustpad assemblies includes a forward thrust pad assembly and a rear thrustpad assembly; and wherein each said saddle forward thrust pad assemblyis sufficiently spaced from said saddle rear thrust pad assembly.
 5. Thecarriage assembly guide bearing assembly of claim 4 wherein each saidsaddle number of thrust pad assemblies includes one medial thrust padassembly.
 6. The carriage assembly guide bearing assembly of claim 5wherein: each said journal channel includes a generally square C-shapedchannel; each said saddle has a parallelepiped cross-section with anupper surface, an outer lateral surface, and a lower surface; and eachsaid saddle thrust pad includes an upper pad portion, a lateral padportion, and a lower pad portion.
 7. The carriage assembly guide bearingassembly of claim 6 wherein: each said guide bearing assembly includes aunitary upper pad member, a unitary lateral pad member, and a unitarylower pad member; each said upper pad member defining a forward thrustpad assembly upper pad portion, a medial thrust pad assembly upper padportion and a rear thrust pad assembly upper pad portion; each saidfirst lateral pad member defining a forward thrust pad assembly lateralpad portion, a medial thrust pad assembly lateral pad portion and a rearthrust pad assembly lateral pad portion; and each said lower pad memberdefining a forward thrust pad assembly lower pad portion, a medialthrust pad assembly lower pad portion and a rear thrust pad assemblylower pad portion.
 8. The carriage assembly guide bearing assembly ofclaim 3 wherein each said carriage assembly guide bearing assemblyincludes a fluid distribution assembly structured to provide a balancedfluid flow to said number of thrust pad assemblies.
 9. The carriageassembly guide bearing assembly of claim 8 wherein: said fluiddistribution assembly includes a number of fluid passages; and wherein anumber of said first fluid distribution assembly fluid passages areselectively closable.
 10. The carriage assembly guide bearing assemblyof claim 2 wherein each said saddle includes a forward thrust padassembly, at least one medial thrust pad assembly, and a rear thrust padassembly.
 11. A can bodymaker comprising: a die pack defining a passage;a housing assembly; a ram assembly including an elongated ram body andan outboard guide bearing assembly; said outboard guide bearing assemblyincluding a carriage assembly; said carriage assembly including a bodywith a ram coupling and a number of guide bearing assemblies; said rambody coupled to said carriage assembly ram coupling; wherein saidcarriage assembly body is structured to travel generally in a plane andto reciprocate between a retracted, first position and a forward, secondposition; and wherein said carriage assembly number of guide bearingassemblies are structured to orient said ram body with said die packpassage.
 12. The can bodymaker of claim 11 wherein: each said carriageassembly guide bearing assembly including a first component and a secondcomponent; each said carriage assembly guide bearing assembly firstcomponent coupled to a carriage assembly body lateral surface; and saidcarriage assembly guide bearing assembly second component coupled tosaid bodymaker housing assembly.
 13. The can bodymaker of claim 12wherein: each said carriage assembly guide bearing assembly firstcomponent is a saddle; and each said carriage assembly guide bearingassembly second component is a journal channel.
 14. The can bodymaker ofclaim 13 wherein: each said saddle includes a number of thrust padassemblies; and each said saddle structured to produce a sufficientamount of fluid to establish an aligning fluid bearing stiffness. 15.The can bodymaker of claim 14 wherein: each said saddle number of thrustpad assemblies includes a forward thrust pad assembly and a rear thrustpad assembly; and wherein each said saddle forward thrust pad assemblyis sufficiently spaced from said saddle rear thrust pad assembly. 16.The can bodymaker of claim 15 wherein each said saddle includes onemedial thrust pad assembly.
 17. The can bodymaker of claim 16 wherein:each said journal channel includes a generally square C-shaped channel;each said saddle has a parallelepiped cross-section with an uppersurface, an outer lateral surface, and a lower surface; and each saidsaddle thrust pad includes an upper pad portion, a lateral pad portion,and a lower pad portion.
 18. The can bodymaker of claim 17 wherein: eachsaid saddle includes a unitary upper pad member, a unitary lateral padmember, and a unitary lower pad member; each said saddle upper padmember defining a forward thrust pad assembly upper pad portion, amedial thrust pad assembly upper pad portion and a rear thrust padassembly upper pad portion; each said saddle lateral pad member defininga forward thrust pad assembly lateral pad portion, a medial thrust padassembly lateral pad portion and a rear thrust pad assembly lateral padportion; and each said first saddle lower pad member defining a forwardthrust pad assembly lower pad portion, a medial thrust pad assemblylower pad portion and a rear thrust pad assembly lower pad portion. 19.The can bodymaker of claim 14 wherein each said carriage assembly guidebearing assembly includes a fluid distribution assembly structured toprovide a balanced fluid flow to said number of thrust pad assemblies.20. The can bodymaker of claim 19 wherein: each said fluid distributionassembly includes a number of fluid passages; and wherein a number ofsaid fluid distribution assembly fluid passages are selectivelyclosable.
 21. The can bodymaker of claim 13 wherein: said first saddleincludes a forward thrust pad assembly, at least one medial thrust padassembly, and a rear thrust pad assembly; and said second saddleincludes a forward thrust pad assembly, at least one medial thrust padassembly, and a rear thrust pad assembly.